JP4455858B2 - Torsion damper - Google Patents

Torsion damper Download PDF

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Publication number
JP4455858B2
JP4455858B2 JP2003339351A JP2003339351A JP4455858B2 JP 4455858 B2 JP4455858 B2 JP 4455858B2 JP 2003339351 A JP2003339351 A JP 2003339351A JP 2003339351 A JP2003339351 A JP 2003339351A JP 4455858 B2 JP4455858 B2 JP 4455858B2
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torsion damper
drive plate
plate
coil spring
portion
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JP2003339351A
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JP2005106158A (en
Inventor
聡 中垣内
勝 江端
伸樹 深谷
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アイシン精機株式会社
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/127Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs using plastics springs combined with other types of springs
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00Springs
    • F16F1/02Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/04Wound springs
    • F16F1/12Attachments or mountings
    • F16F1/128Attachments or mountings with motion-limiting means, e.g. with a full-length guide element or ball joint connections; with protective outer cover

Description

  The present invention relates to a torsion damper of a torsional vibration absorber, and more particularly to a vibration absorber used in a flywheel, a clutch disk or a drive shaft system in order to absorb torque fluctuations of a combustion engine and an electric motor. It relates to torsion dampers.

As a conventional torsion damper for a torsional vibration absorber, there is a torsion damper disclosed in Japanese Patent Application Laid-Open No. 9-229138. This torsion damper is loosely fitted inside a coil spring arranged in the relative rotational direction as an elastic means arranged between a drive plate connected to a drive source and a driven plate connected to a driven source. A substantially cylindrical cushion molded from an elastic resin material. The outer diameter guide portion of the torsion damper is formed smaller than the inner diameter of the coil spring by a predetermined clearance in order to allow smooth expansion and contraction of the coil spring. Further, the central portion is formed to have a smaller diameter than both end portions so that a portion deformed to the outside by the compression when the torsion damper is compressed does not contact the coil spring.
JP-A-9-229138

  However, the torsion damper disclosed in Patent Document 1 has a configuration in which the central portion is made small in diameter in consideration of deformation of the central portion during compression and the guide portions are provided at both ends, so that the length of the necessary elastic portion is secured. And there was a limit in ensuring the length of the guide portion in the axial direction.

  On the other hand, torsional vibration absorbers such as flywheel dampers and clutch disks equipped with such a torsion damper have an increased relative torsion angle between the drive plate and the driven plate in order to achieve high torque performance and the like. There is a need to shorten the length or to set the winding pitch of the coil spring used in the damper mechanism large. In addition, in the coil spring in which the spring characteristics are variable depending on the compression amount, the winding pitch is made unequal, and there is a place where the winding pitch is set large.

  In these cases, as shown in FIG. 8, the torsion damper 110 may fall into the gap d between the coil springs when not compressed, and the torsion damper may be destroyed when the coil spring 10 is compressed.

  Therefore, it is a technical object of the present invention to provide a torsion damper for a torsional vibration absorbing device that solves the above-described problems.

In order to solve the above problem, the technical means taken in claim 1 is a coil spring disposed in a window hole provided in a drive plate connected to a driving source and a driven plate connected to a driven source. And a guide portion formed with a predetermined clearance with respect to the inner diameter of the coil spring, and the drive plate and the driven plate directly to the drive plate during relative rotation of the drive plate and the driven plate at a predetermined angle. In the torsion damper having a cushion portion that abuts on the target or indirectly and transmits an impact torque between the drive plate and the driven plate, a plurality of ribs having an outer diameter substantially equal to the guide portion are the guide portion. extending along the axial direction from, and, and Rukoto extends radially outwardly from the cushion portion It was.

According to the first aspect of the present invention, since the plurality of ribs are extended in the axial direction from the guide portions disposed at both ends of the conventional configuration so as to have the same outer diameter as the guide portions, The torsion damper can be provided in which the rib setting length is not limited, a sufficient length can be secured with respect to the gap between the coil springs, and the fall of the coil spring between the gaps is avoided. In addition, since a space is formed in the portion where the rib of the central portion of the torsion damper is not formed, deformation when the torsion damper is compressed is allowed in this space, and the outer diameter of the guide portion and the rib changes. It wo n’t happen.

  1 and 2 show a disk damper 1 which is an example of a torsional vibration absorber disposed between an engine and a transmission of a vehicle to which the torsion damper of the present invention is applied. 1 is a front view in which a part of a disk damper is cut away, and FIG. 2 is a sectional view taken along line XX in FIG. Friction members 21 and 22 which are bonded and fixed to both sides of the outer periphery of the disk damper 1 (which can be fixed by rivets) are connected to a flywheel (not shown) connected to a crankshaft of an engine as a drive source, It is clamped by a pressure plate (not shown) biased by a disc spring of a limiter that serves to limit the transmission torque bolted to the wheel, and rotates integrally with the flywheel by friction engagement. On the other hand, the hub 30 of the disk damper 1 is spline-fitted to an input shaft (not shown) of a transmission that is a driven element (driven source). Accordingly, the disk damper 1 transmits torque generated between the flywheel and the input shaft.

  The hub 30 of the damper disk 1 has a flange portion 31 extending in the radial direction. On the outer peripheral portion of the flange portion 31, accommodating portions 32 for accommodating the coil springs 10 are formed at a plurality of locations (four equally spaced locations) on the circumference, and the coil springs 10 are disposed at both ends of the accommodating portion 32 via seats 40. To accommodate. Then, the torsion damper 100 is loosely inserted into the coil spring 10. Further, the coil spring 10 is pressed through the seat 40 by the wall 33 of the housing portion 32 when the hub rotates.

  Friction materials 21 and 22 are caulked and fixed by rivets on both surfaces of the outer peripheral portion of the drive plate 51 of the disk damper 1. Further, the drive plate 51 is caulked and fixed by a sub drive plate 52 and a rivet 53 on the inner peripheral side of the friction materials 21 and 22, and the drive plate 51 and the sub drive plate 52, the flange portion 31 of the hub 30, and the coil The spring 10 is sandwiched. The drive plate 51 and the sub drive plate 52 are pivotally supported by the hub 30 so as to be relatively coaxial with each other via a bush and a thrust member 60 that also serve as bearings. The integrally formed drive plate 51 and sub drive plate 52 correspond to the accommodating portion 32 that accommodates the coil spring 10 formed in the flange portion 31 of the hub 30 and extends in a substantially circumferential direction or a tangential direction. Holes 54 and 55 are formed to accommodate the coil spring 10 via the seat 40. The window holes 54 and 55 also press the coil spring 10 through the seats 40 at the walls 56 and 57 when the drive plate 51 rotates, similarly to the housing portion of the hub 30.

  The torque transmission of the damper disk 1 configured as described above will be described. The torque transmitted from the engine or motor to the flywheel during acceleration of the automobile is applied to the drive plate 51 and the sub drive plate 52 by the frictional engagement force generated when the friction materials 21 and 22 are sandwiched between the flywheel and the pressure plate. As a result, relative rotation occurs between the drive plate 51 and the hub 30, and the walls 56 and 57 of the window holes 54 and 55 press one end of the coil spring 10 through the seat 40 to compress the coil spring 10. The other end of the compressed coil spring 10 presses the wall 33 of the housing portion 32 formed on the flange portion 31 of the hub 30 via the seat 40 by a restoring force, and transmits torque to the hub 30. Torque is input to the input shaft of the transmission. On the other hand, reverse torque generated at the time of deceleration or the like is also transmitted from the hub 30 to the drive plate 51 through the coil spring 10 through the reverse path.

  Furthermore, in torque transmission, the relative rotation between the drive plate 51 and the hub 30 increases due to a sudden torque fluctuation generated between the engine and the input shaft due to a shift change of the automobile or a sudden torque increase generated by the drive source. In this case, when the relative rotation proceeds and the relative rotation angle reaches a predetermined value, the contact portions 41 of the sheets disposed at both ends of the coil spring 10 and the torsion damper 100 abut, and the torsion damper 100 is elastically deformed. The torque is transmitted via the torsion damper 100. Further, the peak value of the impact torque generated at the time of contact is suppressed by the elasticity of the torsion damper 100.

  The torsion damper 100 which is a main part of the present invention will be described in detail. The torsion damper 100 is a generally cylindrical cushion that is injection-molded from an elastic resin (for example, a thermoplastic polyester elastomer or the like is fried). The outer diameter of the torsion damper 100 is smaller than the inner diameter of the coil spring 10 (for example, about 0.6 mm smaller in diameter) and is loosely inserted into the coil spring 10. When the relative rotation between the drive plate 51 and the hub 30 reaches a predetermined value, the torsion damper 100 abuts against the abutting portion 41 of the seat and elastically deforms to transmit torque, and at the time of abutment due to the elasticity of the torsion damper 100 Relieve shock. In addition, the small diameter portion is formed in consideration of the amount of deformation when compressed.

Hereinafter, the torsion damper will be described.

  FIG. 3 shows the shape of the torsion damper 300, FIG. 3 (a) is a front view, and FIG. 3 (b) is a cross-sectional view taken along line AA of FIG. In the torsion damper 300, guide portions 301 are set at both ends in consideration of a clearance between coil springs, and a space 303 extending circumferentially through the cushion portion 302 and penetrating in the axial direction is formed at one end. Four places are formed. When the torsion damper 300 is compressed, the deformed portion enters the space 303 and the change in the outer diameter of the guide portion 301 is suppressed.

FIG. 4 is a cross-sectional view of another torsion damper 400 , in which guide portions 401 are set at both ends in consideration of a clearance between coil springs, and a circle is formed between the center side of the guide portion 402 and the cushion portion 402. A space 403 is provided on the circumference.

FIG. 5 shows a cross-sectional view of another torsion damper 500. The guide portion 501 extends from the center portion with the cushion portion 502 in consideration of the gap between the coil springs, and is open at both ends. 504 is provided.

FIG. 6 shows a side view of a torsion damper 600 according to an embodiment of the present invention . The ribs 604 having the same outer diameter as the outer periphery of the guide portion from the guide portions 601 at both ends are directed to four locations at one end and to the central portion. It is formed so as not to fall into the clearance of the coil spring. Further, when the torsion damper 600 is compressed, a portion where the rib 604 is not formed allows a deformed portion, and deformation of the guide portion 601 is suppressed.

  FIG. 7 shows a side view of a torsion damper 700 according to another embodiment, in which a rib 704 extends from a guide portion 701 at one end to a multi-end guide portion 701, and a notch is provided at the center portion. A portion where the rib 704 is not formed allows the deformed portion, and deformation of the guide portion 701 is suppressed.

  As mentioned above, although the shape of the torsion damper of a plurality of the present invention was illustrated, the shape is not limited to these, and if the configuration and shape are based on the present invention and take into account the clearance between the coil springs, the present invention Within the scope of

It is a figure which shows one Embodiment of the torsional vibration absorber using the torsion damper of this invention. It is XX sectional drawing of FIG. It is the front view and sectional drawing (AA) of a torsion damper. It is other sectional drawing of a torsion damper. It is other sectional drawing of a torsion damper. It is a side view which shows other implementation of the torsion damper concerning this invention. It is a side view which shows other implementation of the torsion damper concerning this invention. It is a figure which shows the malfunction of the conventional torsion damper.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Torsional vibration absorber 10 ... Coil spring 40 ... Sheet 41 ... Contact part 110,100,200,300,400,500,600,700 ... Torsion damper 101,201, 301, 401, 501, 601, 701 ... Guide part 102, 202, 302, 402, 502, 602, 702 ... Cushion part

Claims (1)

  1. The coil plate is loosely inserted into a coil spring disposed in a window hole provided in a drive plate connected to the driving source and a driven plate connected to the driven source, and has a predetermined clearance with respect to the inner diameter of the coil spring. And a guide portion formed with the drive plate, and the drive plate and the driven plate at the time of relative rotation at a predetermined angle, abutting directly or indirectly against the drive plate and the driven plate, and an impact torque between the drive plate and the driven plate in torsion damper having a cushion portion for transmitting a plurality of ribs having a substantially equal outer diameter and front Symbol guide portion, extending along the axial direction from the guide portion and, radially outward from the cushion portion a torsion damper according to claim Rukoto extend.
JP2003339351A 2003-09-30 2003-09-30 Torsion damper Active JP4455858B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2003339351A JP4455858B2 (en) 2003-09-30 2003-09-30 Torsion damper

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2003339351A JP4455858B2 (en) 2003-09-30 2003-09-30 Torsion damper
US10/950,642 US7445553B2 (en) 2003-09-30 2004-09-28 Damper disc assembly
EP20040023219 EP1521002B1 (en) 2003-09-30 2004-09-29 Damper disc assembly
CNB2004100833401A CN100408881C (en) 2003-09-30 2004-09-30 Damper disc assembly

Publications (2)

Publication Number Publication Date
JP2005106158A JP2005106158A (en) 2005-04-21
JP4455858B2 true JP4455858B2 (en) 2010-04-21

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JP2003339351A Active JP4455858B2 (en) 2003-09-30 2003-09-30 Torsion damper

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US (1) US7445553B2 (en)
EP (1) EP1521002B1 (en)
JP (1) JP4455858B2 (en)
CN (1) CN100408881C (en)

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EP1780434A3 (en) * 2005-10-29 2009-01-14 LuK Lamellen und Kupplungsbau Beteiligungs KG Clutch device
US9944144B2 (en) 2010-02-23 2018-04-17 Renton Coil Spring Company Spring and damper systems for attenuating the transmission of energy
US9689451B2 (en) 2010-02-23 2017-06-27 Renton Coil Spring Co. Tension spring mount
DE112011100918A5 (en) * 2010-03-15 2013-01-03 Schaeffler Technologies AG & Co. KG A torsional vibration damper
JP5625676B2 (en) * 2010-09-24 2014-11-19 アイシン精機株式会社 Torque fluctuation absorber
JP5714385B2 (en) * 2011-03-31 2015-05-07 アイシン精機株式会社 Torque fluctuation absorber
US10203020B2 (en) 2012-12-20 2019-02-12 Schaeffler Technologies AG & Co. KG Centrifugal pendulum
CN103072139B (en) * 2013-01-21 2015-02-11 上海理工大学 Four-shaft rotation angle keeping mechanism for six-shaft industrial robot
JP6209850B2 (en) * 2013-04-25 2017-10-11 アイシン精機株式会社 Damper device
JP6559399B2 (en) * 2014-02-27 2019-08-14 株式会社エクセディ Damper device
CN105090435A (en) * 2014-04-15 2015-11-25 福特全球技术公司 Vehicle flexible drive plate with torsion damper
CN108138903B (en) * 2015-11-26 2020-03-20 舍弗勒技术股份两合公司 Centrifugal force pendulum

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US330445A (en) * 1885-11-17 Oae seeing
US937346A (en) * 1908-04-10 1909-10-19 Westinghouse Electric & Mfg Co Resilient connection.
DE2727725C2 (en) * 1977-06-21 1985-06-05 Fichtel & Sachs Ag, 8720 Schweinfurt, De
US4148200A (en) * 1978-06-05 1979-04-10 General Motors Corporation Torsional vibration damper for a lock-up clutch
US4714448A (en) * 1984-12-27 1987-12-22 Valeo Torsional damper device
JPH0326341Y2 (en) * 1986-10-15 1991-06-07
JPH07293578A (en) * 1994-04-25 1995-11-07 Daikin Mfg Co Ltd Torsion damper for damper disc
FR2738319B1 (en) * 1995-09-04 1997-10-24 Valeo Double shock absorber with variable straightness
JP3731236B2 (en) 1996-02-28 2006-01-05 アイシン精機株式会社 torsion damper
US6227976B1 (en) * 1999-01-06 2001-05-08 Ulrich Rohs Torsional vibration damper
JP2002340095A (en) * 2001-05-15 2002-11-27 Exedy Corp Damper mechanism
JP2003278836A (en) * 2002-03-26 2003-10-02 Aisin Seiki Co Ltd Torque variation absorption equipment
JP2003278792A (en) * 2002-03-26 2003-10-02 Aisin Seiki Co Ltd Torsion buffer disk

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Publication number Publication date
JP2005106158A (en) 2005-04-21
US20050070363A1 (en) 2005-03-31
EP1521002B1 (en) 2012-06-13
CN1603654A (en) 2005-04-06
CN100408881C (en) 2008-08-06
US7445553B2 (en) 2008-11-04
EP1521002A2 (en) 2005-04-06
EP1521002A3 (en) 2010-03-03

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